WO2005035294A1 - Antriebsstrang und verfahren zum steuern und regeln eines antriebsstranges - Google Patents
Antriebsstrang und verfahren zum steuern und regeln eines antriebsstranges Download PDFInfo
- Publication number
- WO2005035294A1 WO2005035294A1 PCT/EP2004/010551 EP2004010551W WO2005035294A1 WO 2005035294 A1 WO2005035294 A1 WO 2005035294A1 EP 2004010551 W EP2004010551 W EP 2004010551W WO 2005035294 A1 WO2005035294 A1 WO 2005035294A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- clutches
- drive
- drive train
- transmission
- Prior art date
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
- B60K23/08—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles
- B60K23/0808—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles for varying torque distribution between driven axles, e.g. by transfer clutch
Definitions
- the invention relates to a drive train of a vehicle with at least two drivable vehicle axles and with a main transmission arranged between a drive machine and the vehicle axles, and a method for controlling and regulating such a drive train according to the features of the preamble of patent claim 10.
- a drive torque generated by a drive machine is directed to the drive wheels via a transmission as required. If vehicles such as all-wheel drive PK s or all-wheel drive K s are designed with a plurality of driven axles, the power of the drive machine in the drive train of such a vehicle is distributed over the individual drive axles and the various drive wheels.
- differential gears longitudinal differential gears being used in the direction of travel for longitudinal distribution of the drive power of the drive machine to a plurality of driven vehicle axles.
- transverse differentials or differential gears are provided with respect to the direction of travel of a vehicle for a transverse distribution of the drive power on drive wheels of a vehicle axle.
- differential gears conventionally used in practice are so-called bevel gear differentials, spur gear differentials in ' planetary design or Schneckenraddifferentiale.
- spur gear differentials are mostly used as longitudinal differentials because of the possibility of asymmetrical torque distribution.
- Bevel gear differentials are now standard for transverse compensation in vehicles.
- Worm gear differentials are used both for longitudinal distribution and for 'transverse distribution'.
- differential-t-controlled all-wheel drive or all-wheel drive systems is the torque distribution to the front and the rear axle by a planetary gear or a Kegelradifferential.
- planetary gear differentials the drive torque can be distributed as desired between the two drive axles or vehicle axles by selecting the gear ratio.
- Common torque distributions between the front and rear axles are 50%: 50% to 33%: 66%.
- bevel gear differentials the torque distribution is fixed at 50%: 50%. By choosing a fixed torque ratio between the front and rear axles, the distribution of tractive power is only ideal for one point, the design point.
- the drive torque is therefore not divided proportionally to the axle load corresponding to the current driving condition. If the traction reserves are to be fully utilized in the event of high slip, which is theoretically only possible with variable torque distribution between the front and rear axles, the longitudinal differential can be braked or locked. Due to a continuously increasing locking effect with increasing speed difference, such as by means of a viscous lock, the driving behavior is not negatively influenced, and permanent tension in the Drive train, as they occur with positive locks, are avoided.
- clutch-controlled all-wheel drives in which clutches, such as multi-plate clutches, are used with a clutch torque that can be adjusted from the outside.
- the clutch torque can be selected according to the current driving state of the vehicle. In this way it is possible to adapt the torque distribution between the front and rear axles to the dynamic axle load changes, i.e. depending on acceleration, incline, load, etc.
- this object is achieved with a drive train according to the features of patent claim 1 and one Method for controlling and regulating a drive train according to the features of claim 10 solved.
- the inventive power train of a vehicle toy which is designed with at least two drivable vehicle axles and with a main transmission between an engine and the vehicle axles to represent different translations, and in each of the longitudinal drive trains between the main transmission and the 'vehicle axles, a control - And has adjustable friction clutch, the transmission capacity of which can be adjusted via an actuator system, a drive torque of the drive machine can be distributed between the drivable vehicle axles as a function of the variable transmission capabilities of the clutches, one of the clutches for variable distribution of the drive torque slipping between the drivable vehicle axles is operable while another clutch is stable in a synchronous state.
- the transmission capabilities of the two clutches are set such that one of the clutches of the longitudinal drive trains is operated in a synchronous state while the other clutch operated slipping the efficiency of the drive train can be improved in a simple manner.
- the transmission capacity of the clutch which is operated slackly, is varied between a lower limit value and an upper limit value, which corresponds to a synchronous state of the second clutch.
- the starting torque is in any ratio, d-. H. with degrees of distribution of the drive torque between 0% and 100%, can be distributed between the drivable vehicle axles as required and optimized for efficiency.
- Fig.l is a highly schematic representation of a drive train of a vehicle according to the invention.
- FIG. 2 shows a graphical representation of a relationship between the transmission capabilities of the clutches of the drive train according to FIG. 1 and a degree of distribution of the drive torque between two drivable vehicle axles of the drive train;
- 3 shows a schematic diagram of a first embodiment of an actuator system for setting the transmission capabilities of the two clutches from FIG. 1;
- 4 shows a second embodiment of the actuator system for setting the transmission capabilities of the clutches from FIG. 1;
- FIG. 5 shows a third embodiment of the actuator system of the drive train according to the invention.
- FIG. 6 shows a fourth exemplary embodiment of the actuator system, in each case one clutch being drivable by a drive unit;
- FIG. 7 shows a fifth embodiment of the actuator system of the drive train according to the invention.
- the drive train 1 shows a drive train 1 of an all-wheel drive vehicle in a highly schematic representation.
- the drive train 1 comprises a drive unit or an internal combustion engine 2 and a main transmission 3, which can be any transmission known per se from practice.
- main transmission 3 which is intended to represent different translations
- two drivable vehicle axles 4, 5 of the vehicle which are connected in a known manner on each side of the vehicle with at least one drive wheel 6, 7, two clutches k_HA and k_VA in longitudinal drive trains 1_HA and 1_VA arranged, ie between the main transmission 3 and devices 8, 9 for compensating for differential speeds between the drive wheels 6 of the vehicle axle 4 and the drive wheels 7 'of the vehicle axle 5, which devices 8, 9 are designed here as known cross-transfer gearboxes.
- the drive axles 4 and 5 each supplied part of the drive torque is forwarded via the devices 8, 9 to the drive wheels 6 and 7 and distributed between the drive wheels 6 and 7 of the relevant drive axle 4 and 5 as required.
- the two transverse transfer transmissions 8 and 9 offer the possibility of driving the drive wheels ⁇ and 7 of the drive axles 4 and 5 independently of one another in accordance with the different path lengths of the left or right lane at different speeds, as a result of which the drive torque is symmetrical and therefore yaw-free between two drive wheels 6 or 7 of a drive axle 4 or 5 is distributable.
- the two clutches k_HA and k__VA are designed as controllable and controllable frictional multi-plate clutches, the transmission capability of which can be adjusted in each case via an actuator system 10 shown in different versions in FIGS. 3 to 7 and which in the area of a transmission output only one in FIG. 1 schematically illustrated transfer case 11 are arranged. With the clutches k__HA and k_VA, it is possible to distribute a drive torque of the drive machine 2 or transmission output torque of the main transmission 3 variably and as required between the two drivable vehicle axles 4, 5.
- FIG. 2 shows three highly schematic courses, of which a first course gk_VA represents a course of a transmission capacity of the first clutch k__VA between a lower limit value W (u) and an upper limit value W (o).
- a first course gk_VA represents a course of a transmission capacity of the first clutch k__VA between a lower limit value W (u) and an upper limit value W (o).
- Another profile gk_HA represents the profile of the transmission capability of the second clutch k_HA, which corresponds to the profile gk_VA of the first clutch k__VA.
- a third course gvt graphically represents the course of a degree of distribution of the drive torque between the two vehicle axles 4 and 5, the vehicle axle 4 in the present case representing the front axle (VA) and the vehicle axle 5 the rear axle (HA) of an all-wheel drive vehicle.
- the transmission capability of the second clutch k_HA is controlled and regulated in such a way that the clutch k_HA remains in its synchronous state.
- the transmission capacity of the first clutch k_VA is reduced from its lower limit value W (u), at which it does not transmit any torque, in the direction of the upper limit value W (o). speed changed, in which the first clutch k__VA is also in its synchronous state.
- W (u) lower limit value
- W (o) speed changed
- the transmission capability of the first clutch k_VA is regulated and controlled such that the first clutch k_VA is kept in its synchronous state.
- the transmission capacity of the second clutch k_HA is continuously reduced, starting from the upper limit value W (o) of the transmission capacity, at which the second clutch k_HA is synchronous, in the direction of the lower limit value W (u) of the transmission capacity, at which the second clutch k_HA im Essentially no longer transmits torque in the direction of the rear vehicle axle 5.
- the profile gvt of the degree of distribution of the drive torque increases between the Vehicle axles 4 and 5 with increasing reduction in the transmission capacity of the second clutch k_HA up to its maximum value in point III, at which the drive torque is transmitted completely to the front axle 4.
- FIGS. 3 to 7 show five exemplary embodiments of the actuator system 10, which is shown only schematically in FIG. 1, for controlling and regulating the two clutches k__VA and k_HA, the description of FIGS. 3 to 7 for identical and functionally identical Components for clarity, the same reference numerals are used for the sake of clarity.
- the two clutches k_HA and k_VA are each controlled simultaneously by a single actuator 12, whereas the clutches k_VA and k_HA in the embodiment of the actuator system shown in FIG. 7 are each operated separately Actuators 12A and 12B are controlled.
- the actuator system 10 is designed with an electric motor as the actuator 12, whose rotary drive movement can be converted into a linear actuation movement for the clutches k_VA and k__HA by means of a converter device 13.
- the converter device 13 has two ball screws 14 and 15, which are operatively connected to one another, the operative connection of the two ball screws 14 and 15 being formed in that the ball screws 14 and 15 have a common nut 16, which is fixed in the axial direction and can be rotatably driven by the electric motor 12, which is operatively connected to ball screws 14A and 15A with spindles 14B and 15B.
- the spindles 14B and 15B of the ball screw drives 14, 15 are connected in a rotationally fixed manner to components 17 fixed to the housing and are displaceable in the axial direction of the nut 16 such that rotation of the nut 16 in each case results in a translational movement of the spindles 14B and 16 directed in the axial direction of a drive shaft 20 15B results.
- the clutches k_VA and k_HA, or their disk packs 18 and 19, which are designed as multi-plate clutches in the present case, are open or in frictional engagement depending on an axial position of the spindles 14B and 15B of the ball screws 14 and 15.
- Inner plates 18A and 19A of the clutches k_VA and k_HA are connected in a rotationally fixed manner to the drive shaft 20, via which the transmission output torque of the main transmission 2 is applied to the clutches k_VA and k_HA.
- Outer plates 18B and 19B of the clutches k_VA and k_HA are in turn connected to the front axle 4 or the rear axle 5.
- the spindle 15B is moved in the same direction as the spindle 14B by the disk set 19 of the second clutch k_HA, which is synchronous. Initially, nothing changes in the synchronous state of the second clutch k_HA. If the electric motor 12 'continues to drive the nut 16 with the aforementioned direction of rotation, the transmission capacity of the first clutch k_VA is increased until the first clutch k_VA also reaches its synchronous state. At the same time, the contact pressure which is applied by the spindle 15B to the disk set 19 of the second clutch k_HA is steadily reduced, the second clutch k_HA remaining in its synchronous state until point II of the diagram in FIG.
- FIG. 4 shows a further exemplary embodiment of the actuator system 10, the converter device 13 according to FIG. 4 being designed with a single spindle 22 and two separate nuts 16A and 16B in comparison to the converter device 13 according to FIG. 3.
- the one-piece spindle 22 is fixed to the housing-fixed component 17 in a rotational and translational manner, and the nuts 16A and 16B are rotatably connected to the spindle 22 via the ball screw 14A and 15A and are displaceable in the axial direction of the drive shaft 20.
- the nuts 16A and 16B are moved in the same manner as the spindles 14B and 15B shown in FIG. 3 by the rotary drive power of the electric motor 12 towards or away from the disk packs 18 and 19, between the disk packs 18 and 19 of the clutches k_VA and k_HA and the nuts 16A and 16B in the same manner as between the spindles 14B and 15B of the ball screws 14 and 15 according to FIG. 3 and the disk packs 18 and 19, axial needle bearings 23A and 23B and spring devices 24A and 24B, respectively are.
- the axial needle bearings 23A and 23B are provided for the less loss-compensating differential speeds between the spindles 14B and 15B or the nuts 16A and 16B and the disk packs 18 and 19 and for transmitting the contact forces of the converter device 13 to the disk packs 18 and 19.
- the spring means' present in each case represents a suitable means, the Anpresskräf- te of the converter means 19 in a suitable manner on the disk sets 18 and to be able to apply the nineteenth
- the clutches k_VA and k_HA are arranged coaxially to one another and the clutch k_HA is in the
- the converter device 13 of the actuator system 10 according to FIG. 5 is designed only with a ball screw drive 25, which comprises a spindle 25C fixed on the housing side and a nut 25B which can be driven in rotation by the electric motor 12 and is translationally displaceable in the direction of the drive axis 20, the spindle 25C and the Nut 25B are operatively connected via a ball screw 25A.
- the drive shaft 20 is connected to an inner disk carrier 18C of the disk pack 18 of the clutch k_VA and an outer disk carrier 19C of the disk pack 19 of the clutch k_HA.
- the actuator system 10 is designed with a spring system 26, by means of which, depending on a translatory movement of the nut 25B of the ball screw 25, the control and regulation of the clutches k_VA and k_HA described in FIG. 2 can be carried out with only one component 27 which can be moved in translation ,
- the spring system 26 has between the component 27, which rests on the nut 25B or on another axial needle bearing 28, and the inner disks 18A or the outer disks 18B of the disk pack 18 of the first clutch k_VA, between the component 27 and the inner disk carrier 18C of the disk set 18 of the first clutch k_VA and between the component 27 and the inner disks 19A or the outer disks 19B of the disk pack 19 of the second clutch k_HA, springs 26A, 26B, 26C each formed as plate springs.
- the plate springs 26A, 26B and 26C are arranged in such a way that a translational movement of the nut 25B in the direction of the disk packs 18 and 19 of the clutches k_VA and k_HA results in an increase in the contact pressure of the disk pack 18 of the clutch k_VA and a simultaneous reduction in the contact pressure in the disk pack 19 of the clutch k_Ha. If the nut 25B of the ball screw 25 is moved away from the disk packs 18 and 19 of the clutches k_VA and k_HA, the contact pressure on the disk pack 18 of the first clutch k_VA is reduced and the contact pressure on the disk pack 19 of the second clutch k_HA is increased.
- FIG. 6 shows a further exemplary embodiment of the actuator system 10, in which the transmission capabilities of the clutches k_VA and k_HA are provided by a sliding sleeve 29 which is arranged displaceably on the drive shaft 20
- a spring system 26 with springs 26A, 26B and 26C is arranged in each case.
- the contact pressure which depends on an axial position of the sliding sleeve 29
- Spring system 26 is applied to the disk packs 18 and 19 of the clutches k_VA and k_JHA, respectively, is transmitted in a suitable manner by the springs 26A to 26C.
- An actuating lever part 30 engages in the sliding sleeve 29 and can be actuated translationally by the actuator 12 in the directions shown by the double arrow in FIG. 6.
- the actuator 12, which is shown only in a highly schematic manner in FIG. 6, is designed as an electric motor in the present case.
- the rotary drive of the electric motor 12 is transmitted to the actuating lever part 30 to actuate the clutches k_VA and k_HA via a ball screw drive, not shown.
- the spring 26C is provided between a stop 31 and the sliding sleeve 29.
- the spring 26C ensures that the drive torque is transmitted to at least one of the two vehicle axles 4 or 5 and a trip to the next workshop. is possible without all-wheel drive.
- the spring forces of the springs 26A to 26C are coordinated with one another in such a way that the disk set 19 of the second clutch k_HA is acted upon by a pressing force via the sliding sleeve 29 in the event of a failure of the actuator system 10 such that the drive torque is transmitted via the clutch k_HA to the rear axle 5 of the Vehicle or the drive train 1 is guided.
- the clutch k_VA is open and no torque is transmitted to the front axle 4.
- FIG. 7 a further embodiment of the actuator system 10 is shown, in which two actuators 12A, 12B are provided for actuating the clutch k_VA and k HA.
- the actuators 12A and 12B drive the separately executed ball screws 33 and 34 for actuating the clutches k_VA and k_HA.
- the actuation of the actuators 12A and 12B is coupled to one another in this way. pelt that an actuation of one clutch k_VA or k_HA corresponds to the actuation of the other clutch k_HA or k__VA.
- the actuation of the clutches k_VA and k_HA is such that the transmission capacity of the clutch k_VA or the clutch k_HA is varied, while the transmission capacity of the other clutch k_VA or k_HA is kept constant at a value which indicates a synchronous state of this clutch k_HA or k_VA causes.
- the nuts 33A and 33B of the ball screws 33 and 34 are translationally fixed on the drive shaft 20 and rotatably connected to the electric motors 12A and 12B, rotation of the nuts 33A and 34A via ball screws 33B and 34B on spindles 33C and 34C of the ball screws 33 and 34 is transmitted.
- the spindles 33C and 34C are rotationally fixed on the housing side and are arranged on the drive shaft 20 so as to be translationally displaceable in the axial direction of the drive shaft 20 in order to actuate the clutches k_VA and k_HA.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
- Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)
- Retarders (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP04765431A EP1667867A1 (de) | 2003-09-27 | 2004-09-21 | Mehrachsiger antriebsstrang mit kupplungen und verfahren zum steuern und regeln der kupplungen |
US10/573,511 US20070034441A1 (en) | 2003-09-27 | 2004-09-21 | Drive train and method for controlling and regulating a drive train |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10344969A DE10344969A1 (de) | 2003-09-27 | 2003-09-27 | Antriebsstrang und Verfahren zum Steuern und Regeln eines Antriebsstranges |
DE10344969.8 | 2003-09-27 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005035294A1 true WO2005035294A1 (de) | 2005-04-21 |
Family
ID=34353136
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2004/010551 WO2005035294A1 (de) | 2003-09-27 | 2004-09-21 | Antriebsstrang und verfahren zum steuern und regeln eines antriebsstranges |
Country Status (5)
Country | Link |
---|---|
US (1) | US20070034441A1 (de) |
EP (1) | EP1667867A1 (de) |
CN (1) | CN1856414A (de) |
DE (1) | DE10344969A1 (de) |
WO (1) | WO2005035294A1 (de) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007062693A1 (en) | 2005-12-02 | 2007-06-07 | Haldex Traction Ab | Method and system for regulating vehicle dynamics |
DE102005061268A1 (de) * | 2005-12-20 | 2007-06-21 | Gkn Driveline International Gmbh | Reibungskupplung mit Aktuator und Tellerfeder |
DE102005061267B4 (de) * | 2005-12-20 | 2007-12-06 | Gkn Driveline International Gmbh | Differentialanordnung mit zwei gemeinsam betätigten Axialverstellvorrichtungen |
US7584832B2 (en) * | 2005-05-21 | 2009-09-08 | Zf Friedrichshafen Ag | Apparatus for the adjustment capability of two frictional shifting components |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005024757A1 (de) * | 2005-05-31 | 2006-12-07 | Zf Friedrichshafen Ag | Verfahren zur Zu- bzw. Abschaltung des Allradantriebs bei Einsatzfahrzeugen und Arbeitsmaschinen, die keine Längssperren aufweisen |
AT8595U1 (de) * | 2005-07-29 | 2006-10-15 | Magna Drivetrain Ag & Co Kg | Verfahren zum steuern der je einer angetriebenen achse zugeordneten kupplungen eines antriebsstranges mit parkbremsfunktion |
DE102006013542A1 (de) * | 2006-03-24 | 2007-09-27 | Audi Ag | Antriebssystem für allradgetriebene Kraftfahrzeuge |
DE102006025071A1 (de) * | 2006-05-30 | 2007-12-06 | Zf Friedrichshafen Ag | Getriebeeinheit zur Führung eines Antriebsmomentes von einer Antriebswelle auf zwei Abtriebswellen |
DE102006042923B3 (de) * | 2006-09-13 | 2007-10-18 | Audi Ag | Antriebsvorrichtung für allradgetriebene Kraftfahrzeuge |
DE102010014563B4 (de) | 2010-04-10 | 2023-12-28 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Vorrichtung und Verfahren zum Steuern von Anfahrvorgängen von Fahrzeugen mit mehreren Antriebsachsen |
DE102013017579A1 (de) * | 2013-10-24 | 2015-04-30 | Man Truck & Bus Ag | Antriebsstrangmodul für ein Kraftfahrzeug und Montage- und Demontageverfahren für ein Antriebsstrangmodul |
JP6020514B2 (ja) | 2014-05-29 | 2016-11-02 | トヨタ自動車株式会社 | 四輪駆動車両の制御装置 |
CN112277659B (zh) * | 2020-10-26 | 2021-11-09 | 湖北省农业机械工程研究设计院 | 水田装备自适应动力分配系统及方法 |
DE102023200202A1 (de) | 2023-01-12 | 2024-07-18 | Zf Friedrichshafen Ag | Kupplungsanordnung und Antriebsstrang mit Kupplungsanordnung |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH02227339A (ja) * | 1989-06-30 | 1990-09-10 | Mitsubishi Motors Corp | 自動車の動力伝達装置 |
US5358084A (en) * | 1993-01-19 | 1994-10-25 | Chrysler Corporation | Torque magnitude control using electrorheological fluids |
DE19513516A1 (de) * | 1995-04-10 | 1996-10-17 | Fichtel & Sachs Ag | Mehrachsige Antriebsanordnung für ein Kraftfahrzeug |
Family Cites Families (6)
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JPH0649422B2 (ja) * | 1986-12-22 | 1994-06-29 | 株式会社クボタ | 農用トラクタの走行操作構造 |
US5690002A (en) * | 1996-03-06 | 1997-11-25 | Borg-Warner Automotive, Inc. | Method of operating a vehicle differential |
US6484857B2 (en) * | 2001-02-01 | 2002-11-26 | New Venture Gear, Inc. | Torque transfer clutch with ball screw actuator |
US6645109B2 (en) * | 2001-03-27 | 2003-11-11 | New Venture Gear, Inc. | Two-speed transfer case with ball-ramp clutch and single motor activator/shift system |
US6780132B2 (en) * | 2002-08-02 | 2004-08-24 | Visteon Global Technologies, Inc. | Selectively actuated transfer case |
US6848550B2 (en) * | 2003-03-12 | 2005-02-01 | Magna Drivetrain Of America, Inc. | Torque transfer system with two stage ball ramp/clutch actuation |
-
2003
- 2003-09-27 DE DE10344969A patent/DE10344969A1/de not_active Withdrawn
-
2004
- 2004-09-21 CN CNA2004800278647A patent/CN1856414A/zh active Pending
- 2004-09-21 US US10/573,511 patent/US20070034441A1/en not_active Abandoned
- 2004-09-21 EP EP04765431A patent/EP1667867A1/de not_active Withdrawn
- 2004-09-21 WO PCT/EP2004/010551 patent/WO2005035294A1/de not_active Application Discontinuation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02227339A (ja) * | 1989-06-30 | 1990-09-10 | Mitsubishi Motors Corp | 自動車の動力伝達装置 |
US5358084A (en) * | 1993-01-19 | 1994-10-25 | Chrysler Corporation | Torque magnitude control using electrorheological fluids |
DE19513516A1 (de) * | 1995-04-10 | 1996-10-17 | Fichtel & Sachs Ag | Mehrachsige Antriebsanordnung für ein Kraftfahrzeug |
Non-Patent Citations (1)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 0145, no. 40 (M - 1053) 29 November 1990 (1990-11-29) * |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7584832B2 (en) * | 2005-05-21 | 2009-09-08 | Zf Friedrichshafen Ag | Apparatus for the adjustment capability of two frictional shifting components |
WO2007062693A1 (en) | 2005-12-02 | 2007-06-07 | Haldex Traction Ab | Method and system for regulating vehicle dynamics |
DE102005061268A1 (de) * | 2005-12-20 | 2007-06-21 | Gkn Driveline International Gmbh | Reibungskupplung mit Aktuator und Tellerfeder |
DE102005061268B4 (de) * | 2005-12-20 | 2007-09-27 | Gkn Driveline International Gmbh | Reibungskupplung mit Aktuator und Tellerfeder |
DE102005061267B4 (de) * | 2005-12-20 | 2007-12-06 | Gkn Driveline International Gmbh | Differentialanordnung mit zwei gemeinsam betätigten Axialverstellvorrichtungen |
US7699740B2 (en) | 2005-12-20 | 2010-04-20 | Gkn Driveline International Gmbh | Friction coupling with actuator and plate spring |
US7993233B2 (en) | 2005-12-20 | 2011-08-09 | Gkn Driveline International, Gmbh | Friction coupling with actuator and a ball bearing |
Also Published As
Publication number | Publication date |
---|---|
EP1667867A1 (de) | 2006-06-14 |
US20070034441A1 (en) | 2007-02-15 |
CN1856414A (zh) | 2006-11-01 |
DE10344969A1 (de) | 2005-04-21 |
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